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EP0635639A1 - Transmission pour éoliènne - Google Patents

Transmission pour éoliènne Download PDF

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Publication number
EP0635639A1
EP0635639A1 EP94111404A EP94111404A EP0635639A1 EP 0635639 A1 EP0635639 A1 EP 0635639A1 EP 94111404 A EP94111404 A EP 94111404A EP 94111404 A EP94111404 A EP 94111404A EP 0635639 A1 EP0635639 A1 EP 0635639A1
Authority
EP
European Patent Office
Prior art keywords
rotational
primary
planetary
wind
input
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP94111404A
Other languages
German (de)
English (en)
Inventor
David Lior
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ASHOT ASHKELON IND Ltd
Ashot Ashkelon Industries Ltd
Original Assignee
ASHOT ASHKELON IND Ltd
Ashot Ashkelon Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ASHOT ASHKELON IND Ltd, Ashot Ashkelon Industries Ltd filed Critical ASHOT ASHKELON IND Ltd
Publication of EP0635639A1 publication Critical patent/EP0635639A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F16H3/724—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously using externally powered electric machines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D15/00—Transmission of mechanical power
    • F03D15/10—Transmission of mechanical power using gearing not limited to rotary motion, e.g. with oscillating or reciprocating members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D15/00—Transmission of mechanical power
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D9/00—Adaptations of wind motors for special use; Combinations of wind motors with apparatus driven thereby; Wind motors specially adapted for installation in particular locations
    • F03D9/20—Wind motors characterised by the driven apparatus
    • F03D9/25—Wind motors characterised by the driven apparatus the apparatus being an electrical generator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/46—Systems consisting of a plurality of gear trains each with orbital gears, i.e. systems having three or more central gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2270/00—Control
    • F05B2270/10—Purpose of the control system
    • F05B2270/101—Purpose of the control system to control rotational speed (n)
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

  • the present invention relates to wind turbines in general and, more specifically, to improved transmission apparatus for use with wind turbines.
  • Wind turbines are well known in the art.
  • a typical wind turbine includes a wind-powered rotor, a transmission mechanism and an electric generator.
  • the speed conversion ratio of a turbine is normally defined as the rotor speed, in rounds per minute (RPM), divided by the RPM speed of the rotating element in the electric generator.
  • Wind turbine transmissions generally provide a constant (i.e. fixed) transmission ratio.
  • the wind-rotor Due to the generally constant speed conversion ratio of the transmission mechanism and the constrained rotation of the electric generator, the wind-rotor is normally also constrained to a constant speed of rotation. This results in an average loss of approximately 20% of usable wind power, due to aerodynamic inefficiency of the rotor.
  • Wind turbines having fixed-ratio transmission are generally characterized by low fatigue-resistance. It is well known that gusts of wind, which apply high input torques to the wind turbine through the wind-powered rotor, have an accumulatively straining effect on the wind-turbines. Due to the constrained speed of the wind-powered rotor, these sudden energy inputs are not translated into faster rotation of the turbine but, rather, they are internally absorbed by elements of the wind turbine.
  • U.S. Patent 3,140,170 discloses a fluid-driven turbine, including a transmission assembly which is controlled by a hydraulic circuit.
  • the controlled transmission is employed to stabilize the torque exerted on the generator by varying the speed of the rotor relative to the generator. This is achieved by letting the rotor "slip" whenever the torque at the generator exceeds a certain level.
  • this Patent is concerned with controlling the torque at the generator during abrupt acceleration/deceleration of the rotor. When "slipping" of the transmission occurs, substantial amounts of energy are inevitably lost.
  • U.S. Patent 4,695,736 describes a variable speed wind turbine, including an A.C. frequency converter, as described in the preceding paragraph.
  • a preferred embodiment of the present invention provides a transmission mechanism for wind turbines featuring a continuously variable speed conversion ratio.
  • wind turbine transmission apparatus including at least one planetary transmission stage, operative for providing a continuously variable transmission ratio between a rotational input from a wind-rotor and a rotational output to an electric generator. Further, in a preferred embodiment of the present invention, the variable transmission ratio varies substantially in accordance with the velocity of the wind powering the wind turbine.
  • the at least one planetary transmission stage includes a primary planetary stage providing a fixed transmission ratio between the rotational input and a primary rotation, and a secondary planetary stage providing a variable transmission ratio between the primary rotation and the rotational output.
  • the transmission apparatus further includes at least one servo motor operative to receive an electric power input and thereby to provide appropriate rotational power to the at least one planetary transmission stage, when the rotational input is below a preselected rate, and operative to receive appropriate rotational power from the at least one planetary transmission stage and to generate a corresponding electric power output, when the rotational input is above the preselected rate, such that the rotational output remains substantially at a preselected, constant, rate.
  • the appropriate rotational power provided to and/or received from the at least one planetary transmission stage is provided to and/or received from the second planetary stage. additionally or alternatively, the electric power is generated and received through a variable-ratio AC frequency converter.
  • the primary planetary stage includes: an input shaft operative to receive the rotational input; a substantially stationary primary ring gear; a primary planetary arrangement, including a plurality of primary planet gears, associated with the input shaft and rotatable with respect to the primary ring gear; and a primary sun gear for providing the primary rotation, wherein the rotational input is received by the input shaft and transmitted by the primary planetary arrangement to the primary sun gear which, thereby, provides the primary rotation.
  • the secondary planetary stage includes: a rotatable primary ring gear; a secondary planetary arrangement, including a plurality of secondary planet gears, associated with the primary rotation and rotatable with respect to the circumferential ring gear; and an secondary sun gear for providing the rotational output, wherein the primary rotation is received by the secondary planetary arrangement and transmitted to the secondary sun gear which, thereby, provides the rotational output.
  • the secondary ring gear rotates in the same direction as the secondary sun gear, whenever the rotational input is above a preselected rate, and rotates in a direction opposite that of the secondary sun gear, whenever the rotational input is below the preselected rate, such that the rotational output remains substantially at a preselected, constant, rate.
  • the transmission apparatus includes at least one servo motor operative to receive an electric power input and thereby to appropriately rotate the secondary ring gear of the secondary planetary stage when the rotational input is below the preselected rate, and operative to receive appropriate rotational power from the secondary ring gear and to generate a corresponding electric power output when the rotational input is above the preselected rate, such that the rotational output remains substantially at the preselected, constant, rate.
  • a wind turbine including a wind-powered rotor, transmission apparatus as described in the preceding paragraphs wherein the rotational input is a variable-rate rotation received from the wind-powered rotor, and an AC voltage generator operative to receive the rotational output and to provide a corresponding output voltage.
  • the rotational output of the transmission apparatus is at a fixed rate.
  • the corresponding output voltage includes an AC voltage at a fixed frequency.
  • the fixed frequency is 50 Hz or 60 Hz.
  • a wind turbine including a wind-powered rotor, transmission apparatus as described in preceding paragraphs wherein the rotational input is a variable-rate rotation received from the wind-powered rotor, and an AC voltage generator operative to receive the rotational output and to provide a corresponding output voltage to an electric grid, wherein the electric power output of the servo motor is generated to the electric grid and the electric power input is supplied to the servo motor by the electric grid.
  • the wind turbine apparatus includes a wind powered rotor 6 associated, via an input shaft 10, with a variable conversion-ratio transmission apparatus 8, described in great detail hereinbelow, which is associated, in turn, with an alternating current (AC) generator 46.
  • generator 46 supplies, by virtue of supply lines 49, an AC voltage at a preselected, fixed, frequency (typically 50 or 60 Hz) to an AC grid 50.
  • AC grid 50 may be any common AC power network which receives electric power from various generators and supplies electric power to various AC appliances.
  • generator 46 may be the sole generator of a low scale network, such as a private house network, and in such case the AC frequency is not necessarily fixed.
  • grid 50 is preferably further connected, via servo lines 47, to at least one AC servo motor 42 (Fig. 2) of transmission apparatus 8.
  • a variable-ratio AC frequency converter 48 is preferably provided to servo lines 49 for adapting the electric input/output of at least one servo motor 42 to the input/output of grid 50.
  • servo motor 42 either generates or consumes electric power, depending on the rotational speed of wind-powered rotor 6.
  • Fig. 2 illustrates a cross-section of variable conversion-ratio transmission apparatus 8, constructed in accordance with a preferred embodiment of the present invention.
  • transmission apparatus 8 is driven by input shaft 10, which is associated with wind-powered rotor 6 as explained above.
  • Input shaft 10 is associated, preferably via an internally cogged sleeve 14, with a primary planetary arrangement 12, including a plurality of primary planetary axles 11, located inside a transmission housing 18.
  • Sleeve 14 provides limited relative movement between shaft 10 and arrangement 12 so as to compensate for random misalignments in the system, as well known in the art.
  • transmission housing 18 is preferably sealed from the external environment by a low-friction seal 9 which is fixedly mounted on housing 18 and surrounds the portion of planetary arrangement 12 associated with input shaft 10.
  • An externally cogged primary planet-gear 13 is rotatably mounted, via a low-friction roller bearing 24, on each of axles 11.
  • a low-friction roller bearing 24 there are five primary planet gears 13, associated with five respective axles 11 of planetary arrangement 12, two of which are seen in Fig. 2.
  • Primary planetary arrangement 12 is preferably slidably supported by two circumferential ball bearings 16 which are fixedly connected to transmission housing 18. It should be appreciated that any suitable, low-friction, bearings known in the art may be used as bearings 24 and 16.
  • Transmission apparatus 8 further includes an internally cogged circumferential ring-gear 20 which engages the external cogs on planet-gears 13 of primary planetary arrangement 12.
  • Ring-gear 20 is preferably associated with transmission housing 18 via a circumferential sleeve 22 which allows minuscule radial displacements of ring-gear 20, due to vibrations and or random misalignments in the system, thereby maintaining a substantially equal distribution of loads between ring-gear 20 and planetary gears 13.
  • primary planetary arrangement 12 is rotated by input shaft 10
  • primary gears 13 are forced to rotate about axles 11 due to the cogging engagement of planet gears 13 with circumferential ring-gear 20.
  • ring-gear 20 is substantially at rest.
  • any rotation of rotor 6 results in proportional rotation, at a fixed proportion ratio, of primary sun gear 26.
  • the transmission of rotation from rotor 6 to primary sun gear 26 will be hereinafter referred to as the primary planetary stage.
  • the transmission ratio provided by the primary planetary stage is approximately 4.19 to one, i.e the RPM speed of primary sun gear 26 is approximately 4.19 times that of input shaft 10.
  • a second cogged portion 27 of primary sun gear 26 is circumferentially associated with an internally cogged spherical coupling 28.
  • the cogs of portion 27 are preferably crowned (i.e. rounded) to allow compensation for random misalignments in the system, obtained by minuscule relative displacements between gear 26 and coupling 28.
  • Coupling 28 is fixedly associated with a secondary planetary arrangement 30 including a plurality of secondary axles 31 similar to primary axles 11.
  • An externally cogged secondary planet-gear 32 is rotatably mounted, via a low-friction roller bearing 34, on each of secondary planetary axles 31.
  • secondary planet-gears 32 are similar to primary planet gears 13. However, since primary gears 13 rotate at speeds lower than those of gears 32, gears 13 are generally designed to withstand higher mechanical moments. Thus, the cogs of gears 13 are typically thicker than those of gears 32.
  • Secondary planetary arrangement 30 is preferably slidably supported by two circumferential ball bearings 36, similar to ball bearings 16, which are fixedly connected to transmission housing 18.
  • a secondary circumferential ring-gear 38 similar to primary circumferential gear 20, engages the external cogging of planet-gears 32 of secondary planetary arrangement 30.
  • secondary gear 38 is not supported to housing 18 and, therefore, gear 18 is generally not at rest.
  • the external surface 39 of gear 38 is cogged and engages at least one cogwheel 40, associated with at least one respective servo-motor 42.
  • Secondary gear 41 is associated, via a sleeve 43 similar to sleeve 14, with an output shaft 44, seen also in Fig. 1, which rotates generator 46.
  • output shaft 44 rotates at a preselected controlled RPM-rate which enables generator 46 to generate AC voltage at a preselected, fixed, frequency (preferably 50 or 60 Hz) to grid 50.
  • shaft 44 rotates at a constant, fixed, rate while rotor 6 can rotate substantially independently at a varying rate, preferably in accordance with the speed of the wind. This is achieved by a continuously variable transmission-ratio provided by the secondary planetary stage of the present transmission apparatus.
  • the transmission ratio of the secondary planetary stage is between approximately 7.16:1 to approximately 15:1 (i.e the RPM speed of secondary gear 41 is 7.16 - 15 times that of input primary sun gear 26), depending on the speed of primary gear 26 and, thus, of wind-powered rotor 6.
  • the second planetary stage takes together with the fixed transmission ratio provided by the primary planetary stage, as described above, the second planetary stage provides a variable total transmission-ratio, which varies continuously from approximately thirty to one to approximately sixty to one.
  • all of the above mentioned transmission elements are formed of SAE 9310 carburized steel, in accordance with American Gear Manufacturers Association (AGMA) standard AGMA-11.
  • primary and secondary gears 20 and 38 are preferably formed of nitrated steel, in accordance with AGMA standard AGMA-10.
  • AGMA American Gear Manufacturers Association
  • transmission apparatus 8 is constructed to have a preselected reference transmission- ratio, defined as the transmission ratio of the apparatus when secondary ring-gear 38 is at rest (which is rarely the case). It is appreciated that transmission apparatus 8 operates at the reference transmission ratio, wherein ring 38 is at rest, only when rotor 6 rotates at a predetermined RPM rate "R" corresponding to the preselected reference ratio.
  • gear ring 38 rotates in the same direction as that of secondary sun gear 41, such that the RPM rate of output shaft 44 remains equal to U.
  • gear ring 38 rotates in a direction opposite that of secondary sun gear 41, such that the RPM rate of output shaft 44 remains, again, equal to U.
  • wind gusts are constructively absorbed by the transmission apparatus, thereby providing the wind-turbine with high fatigue-resistance. Since surplus rotational energy is absorbed by servo-motor 42, wind-powered rotor 6 can rotate at the abrupt high rates required by wind gusts. This provision reduces the input torques, thereby, improves the fatigue-resistance of the wind turbine. Furthermore, the rotational energy absorbed by servo motor 42 is translated, as described above, to usable electric energy and supplied to grid 50. In a preferred embodiment of the invention, servo motor 42 is programmed to respond to abrupt changes in the input torque gradients which result from abrupt changes in the speed of rotor 6, due to strong wind gusts.
  • Fig. 3 graphically illustrates the performance of a wind turbine using the variable-ratio transmission apparatus of the present invention, as tested against wind turbines using conventional fixed-ratio transmission apparatus.
  • the graphs of Fig. 3 show the electric power output "P” (in KW) of both types of turbines as a function of wind velocity “V” (in meters per second). Wind velocities are also translated, for convenience, to the corresponding RPM rates of a wind-powered rotor.
  • Graph "A” represents the improved apparatus of the present invention, whereas graph “B” represents a typical "state of the art” wind turbine using an optimally selected constant-ratio transmission.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Power Engineering (AREA)
  • Wind Motors (AREA)
EP94111404A 1993-07-21 1994-07-21 Transmission pour éoliènne Withdrawn EP0635639A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IL10644093 1993-07-21
IL106440A IL106440A0 (en) 1993-07-21 1993-07-21 Wind turbine transmission apparatus

Publications (1)

Publication Number Publication Date
EP0635639A1 true EP0635639A1 (fr) 1995-01-25

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EP (1) EP0635639A1 (fr)
IL (1) IL106440A0 (fr)

Cited By (65)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996011338A1 (fr) * 1994-10-07 1996-04-18 Gerald Hehenberger Engrenage planetaire pour turbine eolienne
WO1996030669A1 (fr) * 1995-03-27 1996-10-03 Chan Shin Systeme a engrenages planetaires de transformation a vitesse variable
WO2000017543A1 (fr) * 1998-09-21 2000-03-30 Roland Davidson Procede et dispositif permet de reguler la vitesse dans des transmissions a rapport d'engrenage eleve
EP1045140A2 (fr) 1999-04-12 2000-10-18 A. Friedr. Flender Ag Boíte de vitesses pour éolienne
EP1045139A2 (fr) 1999-04-12 2000-10-18 A. Friedr. Flender Ag Eolienne
WO2000076055A1 (fr) * 1999-06-04 2000-12-14 Bonus Energy A/S Aerogenerateurs, procede et fonctionnement
US6174254B1 (en) * 1998-12-30 2001-01-16 Hamilton Sundstrand Corporation Continuously variable transmission with control arrangement and for reducing transmission belt slippage
US6176804B1 (en) 1998-06-18 2001-01-23 Valmet Voimansiirto Oy Planetary gear train for a wind power station
EP1283359A1 (fr) * 2001-08-10 2003-02-12 RWE Piller Gmbh Centrale d'énergie éolienne
EP1318329A2 (fr) 2001-12-06 2003-06-11 Winergy AG Transmission pour installation éolienne
EP1359299A4 (fr) * 2001-02-08 2004-04-28 Kawasaki Heavy Ind Ltd Systeme de turbine a gaz uniaxiale
WO2004088132A1 (fr) * 2003-03-31 2004-10-14 Voith Turbo Gmbh & Co. Kg Chaîne cinématique pour transmettre une puissance variable
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WO2005012763A1 (fr) * 2003-08-05 2005-02-10 Andrew Stephen Horsfall Transmission destinee a une machine produisant de l'energie renouvelable
JP2005517123A (ja) * 2002-02-05 2005-06-09 イ サン チョル 風力発電装置
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US7762919B2 (en) 2004-10-05 2010-07-27 Fallbrook Technologies Inc. Continuously variable transmission
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WO2011008466A3 (fr) * 2009-06-30 2011-03-31 Teco-Westinghouse Motor Company Convertisseur de puissance destiné à être utilisé avec un aérogénérateur
US8109854B2 (en) 2003-05-30 2012-02-07 Rem Technologies, Inc. Superfinishing large planetary gear systems
GB2491488A (en) * 2011-06-03 2012-12-05 Romax Technology Ltd Electromechanical driveline with power splitting device
US8845471B2 (en) 2013-01-23 2014-09-30 General Electric Company Variable input synchronous output drivetrain for wind turbine
US8845485B2 (en) 2011-04-04 2014-09-30 Fallbrook Intellectual Property Company Llc Auxiliary power unit having a continuously variable transmission
US8852050B2 (en) 2008-08-26 2014-10-07 Fallbrook Intellectual Property Company Llc Continuously variable transmission
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US8900085B2 (en) 2007-07-05 2014-12-02 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US8996263B2 (en) 2007-11-16 2015-03-31 Fallbrook Intellectual Property Company Llc Controller for variable transmission
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US9086145B2 (en) 2006-11-08 2015-07-21 Fallbrook Intellectual Property Company Llc Clamping force generator
US9121464B2 (en) 2005-12-09 2015-09-01 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US9182018B2 (en) 2008-02-29 2015-11-10 Fallbrook Intellectual Property Company Llc Continuously and/or infinitely variable transmissions and methods therefor
US9239099B2 (en) 2007-02-16 2016-01-19 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US9249880B2 (en) 2007-12-21 2016-02-02 Fallbrook Intellectual Property Company Llc Automatic transmissions and methods therefor
US9273760B2 (en) 2007-04-24 2016-03-01 Fallbrook Intellectual Property Company Llc Electric traction drives
US9279482B2 (en) 2009-04-16 2016-03-08 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US9328807B2 (en) 2007-02-01 2016-05-03 Fallbrook Intellectual Property Company Llc Systems and methods for control of transmission and/or prime mover
US9341246B2 (en) 2005-11-22 2016-05-17 Fallbrook Intellectual Property Company Llc Continuously variable transmission
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US9371894B2 (en) 2007-02-12 2016-06-21 Fallbrook Intellectual Property Company Llc Continuously variable transmissions and methods therefor
US9611921B2 (en) 2012-01-23 2017-04-04 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US9618100B2 (en) 2008-05-07 2017-04-11 Fallbrook Intellectual Property Company Llc Assemblies and methods for clamping force generation
US9677650B2 (en) 2013-04-19 2017-06-13 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US9683638B2 (en) 2005-12-30 2017-06-20 Fallbrook Intellectual Property Company Llc Continuously variable gear transmission
US9683640B2 (en) 2008-06-06 2017-06-20 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US9945456B2 (en) 2007-06-11 2018-04-17 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10047861B2 (en) 2016-01-15 2018-08-14 Fallbrook Intellectual Property Company Llc Systems and methods for controlling rollback in continuously variable transmissions
US10458526B2 (en) 2016-03-18 2019-10-29 Fallbrook Intellectual Property Company Llc Continuously variable transmissions, systems and methods
EP3298685B1 (fr) 2015-05-20 2020-08-12 Voith Patent GmbH Système d'entraînement à vitesse de rotation variable et procédé de démarrage et/ou de fonctionnement d'un système d'entraînement à vitesse de rotation variable
US11174922B2 (en) 2019-02-26 2021-11-16 Fallbrook Intellectual Property Company Llc Reversible variable drives and systems and methods for control in forward and reverse directions
US11215268B2 (en) 2018-11-06 2022-01-04 Fallbrook Intellectual Property Company Llc Continuously variable transmissions, synchronous shifting, twin countershafts and methods for control of same
US11667351B2 (en) 2016-05-11 2023-06-06 Fallbrook Intellectual Property Company Llc Systems and methods for automatic configuration and automatic calibration of continuously variable transmissions and bicycles having continuously variable transmission

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